JP4117482B2 - Oil separator - Google Patents

Description

  The present invention relates to the structure of an oil separator used in a compressor that compresses a refrigerant.

  Conventionally, a centrifugal oil separator as described in Patent Document 1 is known as an oil separator used in a compressor for compressing a refrigerant.

  FIG. 9 shows a configuration of a conventional oil separator 100. The oil separator 100 includes an inner cylinder 110 connected to the refrigerant discharge passage 102, and an outer cylinder 120 that is disposed coaxially with the inner cylinder 110, has a larger diameter than the inner cylinder 110, and has a long axial length. It has a heavy cylindrical structure.

  Between the outer peripheral surface 111 of the inner cylinder 110 and the inner peripheral surface 121 of the outer cylinder 120 is a swirl flow separation unit 130 comprising a cylindrical flow path having the inner peripheral surface 121 as an outer diameter and the outer peripheral surface 111 as an inner diameter. The refrigerant discharged from the compression chamber of the compressor (not shown) flows into the swirling flow separation unit 130 from the refrigerant inlet 131 and causes the swirling flow A (see FIG. 10).

  10 is a cross-sectional view of the cross section taken along the broken line B-B ′ in FIG.

  In the swirling flow separation unit 130, the lubricating oil in the refrigerant is moved to the inner peripheral surface 121 side of the outer cylinder 120 and separated by the centrifugal force of the swirling flow A.

  The separated lubricating oil accumulates at the bottom 122 of the outer cylinder 120 and is discharged from an oil outflow hole 123 provided in the outer cylinder 120 to an oil storage chamber 103 provided outside the outer cylinder 120.

  In the outer cylinder 120, a lower part of the inner cylinder 110 (a space adjacent to the inner cylinder 110 in the axial direction) is a swirl flow reversal chamber 140, and a swirl flow A of the refrigerant from which the lubricating oil is separated by the swirl flow separation unit 130. Is reversed in the swirling flow reversing chamber 140, flows from the lower end of the inner cylinder 110 into the inner cylinder 110, passes through the discharge passage 102 connected to the upper end of the inner cylinder 110, and is discharged from a compressor (not shown). Discharged from the tube.

  By the way, in the centrifugal oil separator as described above, when the flow of the swirling flow A of the discharge gas is reversed in the swirling flow reversing chamber 140, the lubricating oil accumulated in the bottom 122 is wound up and carried to the discharge passage 102. In order to prevent this, it is necessary to increase the axial length L of the swirling flow reversing chamber 140.

However, the axial length L of the swirling flow reversing chamber 140 is preferably short because of the space for mounting the oil separator 100.
Japanese Patent Laid-Open No. 2003-13858

  The present invention has been made in view of the above-described problems, and an object of the present invention is to provide an oil separator in which the axial length of the swirl flow reversing chamber is short and can be miniaturized.

  In achieving the above object, the invention according to claim 1 is an oil separator that separates the lubricating oil in the discharge gas by causing the compressed discharge gas to generate a swirling flow, and the discharge gas flows in, A swirling flow reversing chamber (140) that changes the direction of the swirling flow and guides the swirling flow to the inlet (112) that leads to the outside and has a swirling flow reversing chamber (140) that revolves the swirling flow. The width of the cross section of the channel of the chamber (140) is larger than the outer diameter of the channel of the swirl flow separation unit (130).

  Thereby, in the swirl flow reversal chamber (140), the swirl radius of the swirl flow is larger than that in the swirl flow separation section (130), so the flow velocity of the swirl flow is reduced and the lubricating oil is less likely to be wound up. .

  Therefore, it is not necessary to increase the axial length of the swirling flow reversing chamber (140) in order to prevent the lubricating oil from being rolled up, the axial length of the swirling flow reversing chamber (140) can be shortened, and the oil separator can be made compact. Can be realized.

According to the first aspect of the present invention, the swirl flow separation section (130) is coaxial with the inner cylinder (110) having an inlet (112) leading to the outside provided at the end, and the inner cylinder (110). The swirl flow reversing chamber (140) is provided inside the outer cylinder (120), and is provided between the outer cylinder (120) having a diameter larger than that of the inner cylinder (110) and longer in the axial direction. It is characterized by being.

  By the way, it is desirable that the swirl flow in the swirl flow separation unit (130) is a flow with less turbulence (if the turbulence is strong, the velocity component in the radial direction is strong and the separation characteristic of the lubricating oil is deteriorated), and the flow velocity is high. The stronger the centrifugal force, the better the separation characteristics of the lubricating oil.

Accordingly, in the first aspect of the present invention, the outer cylinder (120) has an inlet (131) into which the compressed discharge gas flows, and in the swirling flow separation portion (130) , the outer cylinder (120) is separated from the inlet (131). The inner diameter of the outer cylinder (120) gradually decreases until reaching the swirling flow reversing chamber (140), and the inner diameter of the outer cylinder (120) increases again when reaching the swirling flow reversing chamber (140). And

  Thereby, in the swirl flow separation unit (130), the swirl radius of the swirl flow is reduced, the flow velocity is increased, and the flow is rectified.

According to a second aspect of the present invention, in the first aspect of the present invention, the outer cylinder (120) is provided with a bottom, and the side wall of the outer cylinder (120) is located at a predetermined distance from the bottom. It is characterized in that a hole (123) is provided .

According to the third aspect of the present invention, the swirl flow flows into the swirl flow separation unit (130) that causes the swirl flow to flow into the discharge gas and the inlet (112) that changes the swirl flow direction and communicates with the outside. An oil separator that separates the lubricating oil in the discharge gas by the swirling flow, and has an inner cylinder (12) that is connected to the outside (112). 110) and an outer cylinder (120) disposed on the outer side of the inner cylinder (110), one end having a cylindrical shape (124) and the other end having a substantially spherical shape (125), and the inner cylinder (110) is The outer cylinder (120) has an inlet (131) into which the compressed discharge gas flows into the cylindrical part (124), and the swirl flow separation is arranged inside the cylindrical part (124). The part (130) includes an outer peripheral surface (111) of the inner cylinder (110) and a cylindrical shape of the outer cylinder (120). The swirl flow reversing chamber (140) is formed in the spherical portion (125) of the outer cylinder (120) and is formed between the inner peripheral surface (121) of the position (124). ) Is larger than the outer diameter of the swirling flow separation section (130).

  Thereby, since there is no corner in the internal shape of the swirl flow reversal chamber (140), the swirl flow that flows from the swirl flow reversal chamber (140) into the inlet (112) of the inner cylinder (110) is less likely to be disturbed, and the swirl flow reversal It is less likely to wind up the lubricating oil accumulated in the chamber (140).

  By the way, when the swirling flow whose direction is changed in the swirling flow reversing chamber (140) flows into the inlet (112) provided at the lower end of the inner cylinder (110), the flow path area rapidly decreases, Loss occurs.

Therefore, in the invention according to claim 4 , in the invention according to claim 1 , the inner cylinder (110) has a diameter in the vicinity of the inlet (112) provided at the end of the inner cylinder (110). (110) It is larger than other parts.

  Thereby, since the flow path area of the flow path from the swirl flow reversal chamber (140) to the inside of the inner cylinder (110) does not rapidly decrease, the pressure loss can be reduced.

  In addition, the code | symbol in the parenthesis attached | subjected to each said means is an example which shows a corresponding relationship with the specific means as described in embodiment mentioned later.

( Reference example )
A reference example for explaining a first embodiment of the present invention to be described later will be described below with reference to FIGS. In addition, the same code | symbol is attached | subjected to the same location as the said conventional structure.

(Configuration of reference example )
FIG. 1 is a cross-sectional view of a compressor 1 to which an oil separator 100 of the present reference example is applied.

  The compressor 1 is connected to a refrigerant suction pipe 2 at an upper part and a refrigerant discharge pipe 3 at a lower part of a side wall. A motor 6 and a middle housing are arranged in order from the top inside a housing 4 having a rotary shaft 5 extending in the vertical direction. 9, the turning scroll 7, the fixed scroll 8, the oil separator 100, and the block 15 are arrange | positioned.

  The refrigerant suction pipe 2 is connected to a low-pressure side refrigerant pipe connected to an evaporator (not shown) of the refrigeration cycle, and protrudes from the upper end of the housing 4.

  The refrigerant discharge pipe 3 is connected to a high-pressure side refrigerant pipe connected to a condenser of a refrigeration cycle (not shown), and protrudes from the lower part of the side wall of the housing 4.

  The rotating shaft 5 is rotatably held by a bearing 5b provided in the middle housing 9 and a bearing 5C provided in the upper part of the motor 6, and a crank portion 5a eccentric to the shaft center by a predetermined amount is provided at the lower end thereof. Is formed.

  The motor 6 is a known electric motor composed of a stator coil 6a fixed to the inner peripheral surface of the housing 4 and a rotor 6b that rotates within the stator coil 6a. The motor 6 rotates the rotating shaft 5 when the stator coil 6a is energized by a control device (not shown).

  The middle housing 9 is installed in the housing 4, holds the above-described bearing 5 b, and forms a back pressure chamber 11 between the back surface of the end plate portion 7 a of the orbiting scroll 7 described later.

  The orbiting scroll 7 includes a disc-shaped end plate portion 7a, a spiral blade portion 7b formed so as to protrude downward in the axial direction from the end plate portion 7a, and a back surface (upward in the axial direction) of the end plate portion 7a. ) Has a boss portion 7c formed thereon. The orbiting scroll 7 is connected to the crank portion 5 a of the rotating shaft 5 by the boss portion 7 c and revolves as the rotating shaft 5 rotates.

  The fixed scroll 8 includes an end plate portion 8a and a spiral blade portion 8b formed so as to protrude upward in the axial direction. When the blade portion 7b and the blade portion 8b mesh with each other, the blade portion 7b and the blade portion A plurality of working chambers 10 that look like crescents when viewed from the axial direction are formed between the working chambers 8b.

  When the rotary shaft 5 rotates and the orbiting scroll 7 revolves, the working chamber 10 opens toward the suction chamber 10 a on the outer periphery of the orbiting scroll 7, and the refrigerant flows into the working chamber 10. Next, the working chamber 10 moves while shrinking toward the center of the orbiting scroll 7 and the fixed scroll 8 while the orbiting scroll 7 revolves, and compresses the refrigerant. When the working chamber 10 reaches the center of the orbiting scroll 7 and the fixed scroll 8, the compressed refrigerant passes through the discharge hole 8 c provided at the center of the end plate portion 8 a of the fixed scroll 8 and enters the discharge chamber 14. Discharged.

  The back pressure chamber 11 is an airtight chamber provided in the middle housing 9 at a portion in contact with the back surface of the end plate portion 7 a of the orbiting scroll 7. The inner peripheral side and the outer peripheral side of the airtight chamber are respectively sealed by seal rings 12. It is sealed. The back pressure chamber 11 is supplied with the lubricating oil separated from the refrigerant by the oil separator 100 via the pressure control valve 13, and urges the orbiting scroll 7 in the axial direction from the back surface by the pressure of the lubricating oil. The thrust force applied to the orbiting scroll 7 by the compression pressure is canceled to reduce the sliding loss between the end plate portion 7a of the orbiting scroll 7 and the middle housing 9.

  The oil separator 100 is disposed in an oil storage chamber 103 constituted by a hole provided in a block 15 disposed below the fixed scroll 8 in the housing 4, and includes an inner cylinder 110 and an outer cylinder 120. This is a swirling flow type oil separator having a double cylindrical structure. In the oil separator 100, the refrigerant discharged into the discharge chamber 14 is guided by the compressed refrigerant inflow path 101, the lubricating oil in the refrigerant is separated, and the refrigerant separated from the lubricating oil is provided in the end plate portion 8 a of the fixed scroll 8. The refrigerant is led to the discharge pipe 3 through the refrigerant discharge path 102. The lubricating oil separated by the oil separator 100 is stored in the oil storage chamber 103 and sent to the pressure control valve 13 through the lubricating oil supply path 13 a provided in the block 15. The oil separator 100 will be described in detail later with reference to FIG.

  The pressure control valve 13 depressurizes the lubricating oil supplied from the lubricating oil supply passage 13a in accordance with the pressure introduced from the suction pressure introduction passage 13c connected to the suction chamber 10a. The pressure is transmitted to the back pressure chamber 11 through the back pressure outflow passage 13b.

  FIG. 3 shows the configuration of the pressure control valve 13. The pressure control valve 13 includes a lid portion 13n, an upper housing 13o, and a lower housing 13p. A piston portion 13h, a first coil spring 13i, a rod 13k, a ball valve portion 13l, A second coil spring 13m is provided.

  The lid portion 13n is a plate-like member having a screw groove on the side surface and provided with a suction pressure introduction port 13f that is a hole penetrating from the upper surface to the lower surface.

  The upper housing 13o has a fitting portion that fits with the lid portion 13n at the upper portion, a cylindrical cylinder portion 13g is formed at the middle portion, and a throttle portion 13j having a smaller inner diameter than the cylinder portion 13g is formed at the lower portion. It is a cylindrical member. A back pressure outflow port 13e, which is a hole penetrating from the outer peripheral surface to the inner peripheral surface, is provided at the lower portion of the side wall of the cylinder portion 13g, and the outer diameter of the lower half of the throttle portion 13j is reduced by one. The tapered surface 13q is formed such that the inner diameter extends from the top to the bottom. The side surface of the lower half of the narrowed portion 13j has a thread groove.

  The lower housing 13p is a cylindrical member having a bottom 13r. In addition, the inner diameter of the upper end is increased by one step, a fitting portion that fits into the thread groove of the narrowed portion 13j is formed on the inner peripheral surface, and a lubricating oil inflow port that is a hole penetrating from the upper surface to the lower surface is formed in the bottom portion 13r. 13d is provided.

  The lubricating oil supply path 13a guides the lubricating oil stored in the oil storage chamber 103 to the pressure control valve 13, and is connected to a lubricating oil inlet port 13d provided in the bottom portion 13r. The lubricating oil supply path 13a is provided in a block 15 described later.

  The suction pressure introduction path 13c is for guiding the pressure in the suction chamber 10a to the pressure control valve 13, and is connected to a suction pressure introduction port 13f provided in the upper part of the lid portion 13r. The suction pressure introduction path 13c passes through the end plate portion 8a of the fixed scroll 8 and is connected to the suction chamber 10a.

  The back pressure outflow passage 13b transmits the pressure of the lubricating oil decompressed by the pressure control valve 13 to the back pressure chamber 11, passes through the block 15, the fixed scroll 8, and the middle housing 9, and passes through the side wall of the cylinder portion 13g. It is connected to the provided back pressure outflow port 13e.

  The cylinder portion 13g is a portion where suction pressure is introduced from a suction pressure introduction port 13f formed at the upper portion of the upper housing 13o.

  The piston part 13h is a plate-like member having the same shape as the inner periphery of the cylinder part 13g that moves up and down in the cylinder part 13g, and a rod 13k protruding in the axial direction of the cylinder part 13g is connected to the lower surface. The rod 13k moves up and down integrally with the piston portion 13h.

  The first coil spring 13i is a coiled spring that is disposed in the cylinder portion 13g and biases the piston portion 13h downward.

  The throttle portion 13j is for depressurizing the lubricating oil supplied from the lubricating oil supply passage 13a into the lower housing 13p. When the piston portion 13h moves up and down, the ball portion 13l connected to the lower end of the rod 13k. And the characteristic of decompressing the lubricating oil supplied into the lower housing 13p changes as the size of the gap with the tapered surface 13r changes.

  The second coil spring 13m is a coiled spring that is installed in the lower housing 13p and biases the ball valve portion 13l upward. The force with which the second coil spring 13m urges the ball valve portion 13l upward is set smaller than the force with which the first coil spring 13i urges the piston portion 13h downward. By this second coil spring 13m, the ball valve portion 13l is arranged with a predetermined gap from the tapered surface 13q.

  When high-pressure lubricating oil flows from the lubricating oil inlet port 13f, the pressure of the lubricating oil passes through the clearance between the ball valve portion 13l and the tapered surface 13q and the throttle portion 13j, and then moves downward through the piston portion 13h. Try to let them. Further, the cylinder portion 13g has the suction pressure introduced from the suction pressure introduction port 13f, and tries to move the piston portion 13h downward by this suction pressure and the elastic force of the first coil spring 13i.

  When the piston portion 13h moves upward, the rod 13k connected to the lower surface of the piston portion 13h is pulled upward, and the gap between the ball valve portion 13l connected to the lower end of the rod 13k and the tapered surface 13q is small. As a result, the lubricating oil is further decompressed. When the lubricating oil is depressurized, the pressure for moving the piston 13h upward decreases.

  As described above, the pressure control valve 13 controls the pressure of the lubricating oil so that the pressure for moving the piston portion 13h upward is balanced with the pressure for moving the piston portion 13h downward.

  As a result, the controlled lubricating oil pressure is maintained at a pressure that is substantially constant higher than the suction pressure. This pressure can be adjusted by the force of the first coil spring 13i.

  On the other hand, the preferable pressure of the lubricating oil is a back pressure that is just enough to cancel the thrust force generated by the compression pressure applied to the orbiting scroll 7, but it is understood that this pressure is a pressure that is almost a constant value higher than the suction pressure. ing. For these reasons, the pressure of the back pressure forming lubricating oil is preferably controlled by the control valve having the characteristics as described above.

  The block 15 is a member made of metal such as iron or aluminum and disposed at the lower end portion inside the housing 4. The oil storage chamber 103, the pressure control valve 13, the lubricating oil supply passage 13 a, the back pressure outflow passage 13 b, and the suction pressure introduction passage 13c.

  Hereinafter, the oil separator 100 which is the oil separator of the present invention will be described in more detail with reference to FIG.

  The oil separator 100 is a double cylinder composed of an inner cylinder 110 connected to the refrigerant discharge path 102 and an outer cylinder 120 that is arranged coaxially with the inner cylinder 110 and has a larger diameter and a longer axial length than the inner cylinder 110. It has a cylindrical structure. The inner cylinder 110 and the outer cylinder 120 are disposed in the oil storage chamber 103.

  The inner cylinder 110 is a cylindrical member whose upper end is connected to the refrigerant discharge path 102 provided on the back surface of the end plate portion 8 a of the fixed scroll 8 and whose lower end is opened.

  The refrigerant discharge path 102 is provided in the end plate portion 8 a of the fixed scroll 8 and is connected to the refrigerant discharge pipe 3. The refrigerant discharge path 102 guides the refrigerant separated from the lubricating oil by the oil separator 100 to the refrigerant discharge pipe 3. is there.

  The outer cylinder 120 is a cylindrical member having an upper end fixed to the back surface of the end plate portion 8 a of the fixed scroll 8 and a bottom portion 122 at the lower end.

  A refrigerant inlet 131 is provided in the upper part of the inner wall of the outer cylinder 120. A compressed refrigerant inflow passage 101 is connected to the refrigerant inlet 131 from the tangential direction of the outer cylinder 120.

  A plurality of oil flow holes 123 are provided below the side wall of the outer cylinder 120. The oil flow hole 123 is a hole that communicates the inside of the outer cylinder 120 and the oil storage chamber 103.

Between the outer peripheral surface 111 of the inner cylinder 110 and the inner peripheral surface 121 of the outer cylinder 120, a cylindrical shape having the inner peripheral surface 121 of the outer cylinder 120 as an outer diameter and the outer peripheral surface 111 of the inner cylinder 110 as an inner diameter (this reference example). In the outer cylinder 120, a lower part of the inner cylinder 110 is a swirl flow reversing chamber 140.

  The diameter of the outer cylinder 120 is smaller than the diameter of the upper part (diameter indicated by C in FIG. 2) of the upper part of the swirl flow separation unit 130 (indicated by D in FIG. 2). The diameter is gradually increased so that it becomes smaller. In other words, the maximum width of the cross section of the swirling flow reversing chamber 140 is larger than the outer diameter of the swirling flow separation section 130 (the inner diameter of the upper portion of the outer cylinder 120).

  The swirling flow separation unit 130 is a portion that causes the swirling flow A to flow from the refrigerant inflow port 131 through which refrigerant and lubricating oil flow in the tangential direction of the outer cylinder 120.

  In the swirling flow separation unit 130, the lubricating oil in the discharge gas is moved to the inner peripheral surface 121 side of the outer cylinder 120 by the centrifugal force of the swirling flow A, and the refrigerant and the lubricating oil are separated.

  Then, the separated lubricating oil is transmitted to the inner peripheral surface 121 and accumulated at the bottom 122, and is discharged to the oil storage chamber 103 from the oil outlet hole 123 provided in the circumferential direction near the bottom 122.

  The swirling flow reversing chamber 140 changes the flow of the swirling flow of the refrigerant from which the lubricating oil has been separated by the swirling flow separating unit 130 and guides it to the inlet 112 leading to the refrigerant discharge path 102.

(Effect of this reference example )
As described above, in this reference example , the diameter of the outer cylinder 120 is lower than that of the upper part (diameter indicated by C in FIG. 2) forming the swirl flow separation unit 130. The diameter (diameter indicated by D in FIG. 2) is larger.

  As a result, the swirl radius of the swirl flow A is larger in the swirl flow reversal chamber 140 than in the swirl flow separation unit 130. As the turning radius increases, the flow velocity of the swirling flow A decreases, and the lubricating oil accumulated in the bottom portion 122 is less likely to be wound up.

  Therefore, it is not necessary to increase the axial length L of the swirl flow reversing chamber 140 in order to prevent the lubricating oil from rolling up, the axial length of the swirling flow reversing chamber can be shortened, and the oil separator 100 can be downsized. It becomes possible.

(First Embodiment)
Next, a first embodiment of the present invention will be described with reference to FIG. In addition, the same code | symbol was attached | subjected to the site | part same as the reference example mentioned above .

In the reference example described above, the diameter of the outer cylinder 120 is set so that the diameter of the lower part forming the swirling flow reversing chamber 140 is larger than the diameter of the upper part forming the swirling flow separation unit 130. Then, the diameter of the outer cylinder 120 is gradually decreased from the top to the bottom from the position where the refrigerant flows from the refrigerant inlet 131 to the swirling flow reversing chamber 140 in the swirling flow separation unit 130, and then the swirling flow reversing chamber. When it reached 140, it gradually increased from top to bottom.

FIG. 4 is a view showing a cross section of the oil separator 100 according to the first embodiment, and the diameter of the outer cylinder 120 is gradually smaller than the diameter of the swirling flow separation unit 130. Specifically, the diameter D2 of the lower part of the swirl flow separation unit 130 is smaller than the diameter D1 of the upper part of the swirl flow separation unit 130. When reaching the swirl flow reversal chamber 140, the diameter C of the outer cylinder 120 gradually increases.

(Effect of this embodiment)
Also in this embodiment, since the swirl radius of the swirl flow A is larger in the swirl flow reversing chamber 140 than in the swirl flow separation unit 130 as in the reference example described above , the flow velocity of the swirl flow A decreases, and the bottom 122 It is less likely to wind up the accumulated lubricating oil.

  By the way, the swirl flow A in the swirl flow separation unit 130 is preferably a flow with less turbulence (if the turbulence is strong, the velocity component in the radial direction is strong and the separation characteristic of the lubricating oil is deteriorated), and the higher the flow velocity, Strong centrifugal force and good separation characteristics.

  In the present embodiment, in the swirling flow separation unit 130, the flow gradually decreases from the position where the refrigerant flows from the refrigerant inlet 131 to the swirling flow reversal chamber 140, so the flow path of the swirling flow A is reduced and the flow velocity is high. And the flow is rectified. Therefore, the swirl flow separation unit 130 exhibits excellent separation characteristics.

Next, a modification of the first embodiment will be described with reference to FIGS.

In the modification shown in FIG. 5, in the first embodiment, the oil outflow hole 123 is provided at a position away from the bottom 122 by a predetermined distance E from the upper side.

  Lubricating oil that accumulates at the bottom 122 scoops up the inner peripheral surface 121 of the outer cylinder 120 to some extent under the influence of the swirl flow A. For this reason, the oil outflow hole 123 does not need to be provided at the lower end portion of the outer cylinder 120, and may be provided above the bottom portion 122 by a predetermined distance E. As a result, even if the amount of the lubricating oil stored in the oil storage chamber 103 increases, it does not flow into the outer cylinder 120 through the oil outflow hole 123, and a large amount of lubricating oil can be stored in the oil storage chamber 103.

In the modification shown in FIG. 6, in the first embodiment, the diameter in the vicinity of the inlet 112 at the lower end of the inner cylinder 110 gradually increases from top to bottom.

  When the swirling flow A whose direction has been changed in the swirling flow reversing chamber 140 flows into the inlet 112 of the inner cylinder 110, the flow path area rapidly decreases, and thus pressure loss occurs. In the modification shown in FIG. 6, in order to reduce this pressure loss, the diameter in the vicinity of the inlet 112 of the inner cylinder 110 is increased from the top to the bottom.

  Thereby, since the flow path area of the flow path from the swirl flow reversal chamber 140 to the inside of the inner cylinder 110 does not rapidly decrease, the pressure loss can be reduced.

(Second Embodiment)
Next a second embodiment of the present invention will be described with reference to FIG. In addition, the same code | symbol was attached | subjected to the site | part same as the reference example mentioned above .

In the outer cylinder 120 of the second embodiment, the upper half is cylindrical (portion indicated by reference numeral 124 in FIG. 7), and the lower half is spherical (part indicated by reference numeral 125 in FIG. 7). The swirl flow separation unit 130 is formed between the outer peripheral surface 111 of the inner cylinder 110 and the inner peripheral surface 121 of the cylindrical portion (124) of the outer cylinder 120. Further, the swirl flow reversing chamber 140 is formed by the inner peripheral surface 121 of the spherical portion (125) of the outer cylinder 120.

  Also in the present embodiment, the maximum width C of the spherical portion 124 of the outer cylinder 120 is such that the maximum width of the cross section of the swirl flow reversing chamber 140 is larger than the inner diameter of the swirl flow separation unit 130. The inner diameter D of the cylindrical portion 125 is larger.

The oil outflow hole 123 is provided at a position where the width of the spherical portion 124 of the swirling flow reversing chamber 140 is maximized. In addition, as in the first embodiment, the inner diameter of the cylindrical portion 124 forming the swirl flow separation unit 130 gradually decreases from top to bottom.

  According to the present embodiment, since the swirl flow reversing chamber 140 has a spherical shape, the flow path in the swirl flow reversing chamber 140 has no corners, so that the swirl flow A flowing into the inlet 112 from the swirl flow reversing chamber 140 is disturbed. Is less likely to occur, and the lubricating oil accumulated in the swirling flow reversing chamber 140 is less likely to be rolled up. Therefore, the axial length of the swirl flow reversing chamber 140 can be shortened, and the overall shape can be reduced.

Further, since the lower half of the outer cylinder 120 has a spherical shape, the height at which the lubricating oil scoops up the inner peripheral surface 121 is increased. Therefore, the oil outflow hole 123 can be installed at a higher position, and the amount of oil stored in the oil storage chamber 103 can be increased compared to the first and second embodiments.

Next, a modification of the second embodiment will be described with reference to FIG.

FIG. 8A shows the second embodiment in an inverted arrangement. When the oil separator is placed upside down, the conventional double cylindrical oil separator as shown in FIG. 9 cannot be placed upside down because there is no site for stably storing the separated lubricating oil.

  However, according to the present invention, the diameter of the outer cylinder 120 is widened from the swirling flow separation unit 130 to the swirling flow reversing chamber 140, and the lubricating oil can be stored in the portion 126 where the outer cylinder 120 spreads. By providing the oil outflow hole 123 in the portion 126 where the outer cylinder 120 is widened, it is possible to exert a sufficient function as an oil separator.

FIG. 8B shows the second embodiment arranged horizontally. Due to the swirling flow remaining in the swirling flow reversing chamber 140, a large amount of lubricating oil gathers at the maximum diameter portion of the spherical portion 125 of the swirling flow reversing chamber 140. Therefore, by providing the oil outflow hole 123 in the maximum diameter portion, it is possible to exhibit a sufficient function as an oil separator even when placed horizontally.

  Further, the generation method of the swirling flow may be any method as long as the swirling flow can be generated.

In the reference example for demonstrating embodiment of this invention, it is sectional drawing of the compressor 1 to which the oil separator 100 is applied. It is sectional drawing which shows the structure of the oil separator 100 in a reference example . The configuration of the pressure control valve 13 is shown. It is sectional drawing which shows the structure of the oil separator 100 in 1st Embodiment. It is sectional drawing which shows the modification of 1st Embodiment. It is sectional drawing which shows the modification of 1st Embodiment. It is sectional drawing which shows the structure of the oil separator 100 in 2nd Embodiment. It is sectional drawing which shows the modification of 2nd Embodiment. It is sectional drawing which shows the structure of the conventional oil separator. It is a figure which shows the principle which a swirl | vortex flow generate | occur | produces.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 100 ... Oil separator, 110 ... Inner cylinder, 120 ... Outer cylinder, 122 ... Bottom part, 123 ... Oil outflow hole, 130 ... Swirling flow separation part, 140 ... Swirling flow inversion chamber, 14 ... Discharge chamber.

Claims (4)

An oil separator that separates lubricating oil in the discharge gas by causing the compressed discharge gas to generate a swirling flow,
A swirl flow separation unit (130) into which the discharge gas flows and causes the swirl flow;
A swirl flow reversing chamber (140) for changing the direction of the swirl flow and guiding the swirl flow to the inlet (112) leading to the outside;
The maximum width of the flow passage cross section of the swirling flow inverting chamber (140), much larger than the flow path outside diameter of the swirling flow separation unit (130),
The swirl flow separation part (130) is arranged coaxially with the inner cylinder (110) having an inlet (112) leading to the outside provided at an end thereof, and the inner cylinder (110). 110) is provided between outer cylinders (120) having a diameter larger than 110 and long in the axial direction,
The swirl flow reversing chamber (140) is provided in the outer cylinder (120),
The outer cylinder (120) has an inlet (131) into which the compressed discharge gas flows,
In the swirling flow separation section (130), the inner diameter of the outer cylinder (120) gradually decreases from the inlet (131) to the swirling flow reversing chamber (140), and the swirling flow reversing chamber (140). ), The inner diameter of the outer cylinder (120) is increased again . The said outer cylinder (120) is provided with the bottom part, The hole (123) is provided in the position away from the said bottom part at the side wall of the said outer cylinder (120). The oil separator according to 1 . A swirl flow reversing chamber (140) that introduces the swirl flow into the swirl flow separation unit (130) that causes the swirl flow to flow in and changes the direction of the swirl flow and leads to the outside (112) that leads to the outside. An oil separator that separates lubricating oil in the discharge gas by the swirling flow,
An inner pipe (110) provided at an end with an inlet (112) leading to the outside;
An outer cylinder (120) disposed on the outer side of the inner cylinder (110), one end of which is cylindrical (124) and the other end of which is substantially spherical (125);
The inner cylinder (110) is disposed inside the cylindrical part (124),
The outer cylinder (120) has an inlet (131) into which the compressed discharge gas flows into the cylindrical part (124),
The swirl flow separation portion (130) is between the outer peripheral surface (111) of the inner cylinder (110) and the inner peripheral surface (121) of the cylindrical portion (124) of the outer cylinder (120). Formed,
The swirl flow reversal chamber (140) is provided in the spherical portion (125) of the outer cylinder (120),
The oil separator characterized in that the maximum width of the cross section of the flow path of the swirl flow reversing chamber (140) is larger than the outer diameter of the flow path of the swirl flow separation section (130). The inner cylinder (110) has a larger diameter in the vicinity of the inlet (112) provided at the end of the inner cylinder (110) than other parts of the inner cylinder (110). The oil separator according to claim 1 , wherein